DE3723015C2 - - Google Patents

Description

The invention relates to a split flywheel with two coaxial flywheel elements on which the masses the flywheel are essentially divided, and with a part coupling the flywheel elements playful slip clutch and spring arrangement with an intermediate beam coaxial with the flywheel elements, which with a flywheel element over a Slip clutch and with both flywheel elements over separate coil spring groups with different Spring rate is drive coupled, one of the coil spring groups made of springs with a circular screw axis exists, the center of curvature in the flywheel axis falls.

Such a flywheel is known from DE 36 29 225 A1 known.

In this known flywheel, the intermediate carrier can compared to both flywheel elements approximately the same turn far. This is due to the fact that in the case of relative rotations between the flywheel elements and the intermediate carrier springs of the intermediate carrier that are under pressure spring groups coupling with the flywheel elements in Circumferential direction of the flywheel approximately equal lengths exhibit. Otherwise, the range of rotation of the intermediate carrier against the one flywheel element by it arranged bolts or rivets limited, which in the circumferential direction through the elongated holes arranged on the intermediate beam.  Compared to the other flywheel element, one Rotation limit reached that on the inner circumference of the Intermediate teeth with bolts on the other Flywheel element interact.

The stiff spring group, which faces the intermediate beam which elastically supports a flywheel element consists of the springs with the curved coil spring axis. Parallel a slip clutch is effective for this spring group.

The intermediate carrier is opposite the other flywheel element with two parallel spring groups elastic supported, the springs of one connected in parallel Work spring group with play, so that these springs only take effect if the intermediate carrier against the Force of the springs of the other spring group connected in parallel something compared to the other flywheel element twisted.

The spring group with play has a slightly higher one Spring rate as the spring group connected in parallel. Otherwise, the spring groups connected in parallel according to the torsion characteristic shown in DE 36 29 225 A1 together a spring rate, which is lower than the spring rate of the stiff spring group.

Immediately between the flywheel elements are still two slip clutch arrangements effective, one Slip clutch arrangement forms a basic friction, which is always effective while the other slip clutch assembly is playful, such that after it takes effect this slip clutch arrangement in a relative Direction of rotation of the flywheel elements when the direction of rotation is reversed the entire game must first be run through,  before this slip clutch arrangement in the now reverse Direction of the relative rotation takes effect.

This well-known split flywheel cannot be an optimal one Have operational behavior.

At normal operating speeds, such split work Flywheels in the so-called supercritical range, i.e. H. the vibrations excited by the engine or in the drive train have a frequency well above the resonance frequency of the divided flywheel. In this supercritical area there is a vibration separation between engine and Drivetrain optimally reached when the two flywheel elements only elastic, d. H. without effective force connection between them, drive-coupled to each other are.

According to DE 36 29 225 A1, however, between the flywheel elements the basic friction is always effective, d. H. the Both flywheel elements are permanent in mind effective friction clutch parallel to the Coupled spring assemblies. However, this leads to the fact that Operating speeds only an imperfect vibrational There is a separation between the engine and the drive train.

The basic friction mentioned can be used in a construction according to DE 36 29 225 A1 is not readily dispensed with will. The same also applies to the parallel effective clutch arrangement with basic friction. If at normal operating speeds from the engine a torque is transmitted to the drive train, so the flywheel elements against the force of between effective spring arrangements more or less far rotate relative to each other so that the spring groups transmit the respective torque in the respective direction of rotation  can. In the event of a load change, the Flywheel elements a comparatively large relative rotation out before between the flywheel elements effective spring arrangements for torque transmission sufficient tension in the opposite direction exhibit. To the speed of the load changes occurring relative rotation between the flywheel elements limit and to excite vibrations due to briefly successive load changes must avoid the basic friction - just like that parallel acting slip clutch arrangement - have a certain strength.

If inevitably the resonance range when starting the engine of the divided flywheel, is basically advantageous if the flywheel elements powered by very long-stroke and soft springs are coupled. Through a soft coordination of the Springs is namely achieved that the resonance frequency of the divided flywheel is at very low frequencies, so that under certain circumstances even at idle speed Engine is the supercritical area of the split flywheel is achieved, d. H. the excited by the motor or in The drivetrain already has vibrations a frequency above the resonance frequency of the divided Flywheel. The long stroke of the suspension is low Speeds desired to - operation in supercritical Provided area - a vibration separation between drivetrain and engine also compared to the low speed vibrations with large To be able to ensure amplitude.

However, very long-stroke suspension is essential disadvantageous with load changes during normal operating speeds.  

For this reason, the soft spring groups are with the divided flywheel according to DE 36 29 225 A1 comparatively short stroke, so that also in the area of low speeds of the supercritical range only one relatively limited vibration separation between The engine and drive train are present.

The object of the invention is now a divided flywheel with significantly improved operating behavior.

This is the task of a split flywheel solved type in that the stiff Spring group, which the intermediate carrier with one Flywheel element couples, made of short-stroke springs is that the soft spring group, which the intermediate carrier couples with the other flywheel element through which Coil springs with the arcuate screw axis is formed that the springs of the soft spring group so are soft and long stroke that they are dependent on centrifugal force Working by friction by centrifugal force radially outside against bearing surfaces on the intermediate beam or be pushed on the other flywheel element, and that parallel to the soft spring group, only with a larger one Relative rotation between the other flywheel element and effective intermediate suspension and / or the intermediate carrier playful slip clutch is arranged.

The very long-stroke coil springs with a circular arc curved coil spring axis of the soft spring group work at low speed with largely negligible Friction. Because of the softness of these feathers becomes an extremely low resonance frequency of the divided Flywheel reached, so that the idling speed of the engine is clearly in the supercritical range and the resonance frequency of the divided flywheel at most  be stimulated very briefly when starting the engine can. Because of the long stroke of the springs mentioned become comparatively large at low engine speeds Enables relative rotations between the flywheel elements, d. H. even with vibrations with a large amplitude can good vibration isolation between engine and powertrain can be achieved.

Stiffen at normal engine operating speeds the long-stroke helical springs mentioned with a circular arc increasingly curved coil spring axis, because due to the now effective centrifugal force a considerable one Friction occurs between these springs and the bearing surfaces. With a somewhat simplified view, the due to the long-stroke coil springs with the curved Screw axis caused drive coupling between the intermediate carrier and a flywheel element as stiff or non-positive (in the sense of a slip clutch) be viewed as soon as normal operating speeds are available. Accordingly, at these operating speeds stiffening of the flywheel, which extremely desirable with regard to possible load changes is because this will cause larger relative rotations between the flywheel elements avoided during load changes or - at most - with a significantly reduced average relative speed executed. The vibration decoupling between engine and drivetrain can be at the higher Speeds, d. H. when the centrifugal forces take effect solely through the short-stroke springs of the other spring group are guaranteed, because at higher speeds only have vibrations with a higher frequency a low amplitude. Otherwise, due to the stiffening the long stroke springs also prevents the Intermediate carrier torsional vibrations relative to the flywheel elements can perform with large amplitude.  

Due to the type of construction according to the invention the advantage achieved on a between the flywheel elements immediately effective basic friction caused by a constantly effective slip clutch is generated can be d. H. at operating speeds, one can optimal vibration separation between engine and Achieve powertrain.

The stop suspension and / or the clutch with play are only in the flywheel according to the invention with extreme impact loads on the drive train and / or effective if due to starting difficulties of the Motors made several unsuccessful start attempts immediately occur in succession and thereby the resonance frequency of the divided flywheel excited over a long period of time becomes.

In an advantageous embodiment of the invention Spring groups radially one above the other relative to the flywheel axis arranged, the spring group with the long-stroke Springs is preferably housed radially on the outside.

The bearing surfaces for the long-stroke springs are preferred on a flywheel element as U-shaped in cross section or circular bed, the bed on the the springs on the radially outward supporting side with a Sliding layer can be lined. The bed grants that Springs a large-area support, the sliding layer works an excessive increase in friction at high centrifugal forces opposite.

Otherwise, the bed can be filled with lubricant Form an annular chamber. The lubricant carries on the one hand to reduce wear on the springs, on the other hand  acts the hydraulic resistance of the lubricant as a vibration damper.

At the ends of the bearing surfaces can be in each other Axial direction of the flywheel opposite abutment elements be arranged whose distance is less than that The diameter of the long-stroke springs is and which for Flywheel axis tangential, opposite to each other Have cutouts or windows in which as resilient Additional coil springs serving as stops are cage-like are used; there  the intermediate girder engages between the abutments elements movable extensions with play in scope direction in the space between the long stroke springs and the other feathers. This arrangement is more appropriate as equipped so that the extensions mentioned arranged at both ends of the long-stroke springs are and have a distance in the circumferential direction, which corresponds to the distance between the abutment elements. Dementspre The long-stroke springs become corresponding with relative rotation between the one flywheel element or the one swing wheel mass and the intermediate carrier in each case between the contra bearing elements at one end of the springs and one of the fort sets of the intermediate beam compressed while the extension at one end of the feathers, and at larger relative rotation between the one flywheel element or the one flywheel mass and the intermediate carrier the stop suspension interacts.

The preferably additionally between the intermediate carrier and one flywheel element effective playful slip clutch can be in an advantageous design arranged in the area of the inner circumference of the intermediate carrier be spring elements, which friction elements or rings push the clutch against each other, serve at the same time can, a bearing associated with a flywheel element shell of a bearing holding the other flywheel element to hold on.

Otherwise, the preferred features of Invention on the claims and the following description Exercise of a preferred embodiment with reference to the drawing referred.  

It shows

Fig. 1 is a schematic representation of a divided flywheel according to the invention,

Fig. 2 is a diagram for explaining the dependency of between the flywheel masses or elements acting or to be overcome torques (M) in dependence on the relative displacement (Φ) of the flywheel elements

Fig. 3 is an axial section of the flywheel according to the invention,

Fig. 4 is an axial view according to the arrow IV in Fig. 3, the flywheel being shown partially broken away,

Fig. 5 shows a detail V from Fig. 3 and

Fig. 6 is a sectional view along the line VI-VI in Fig. 5.

In Fig. 1, the two flywheel elements 1 and 2 are each shown schematically as heavy bodies which are coupled to one another via a spring arrangement 3 , such that the flywheel elements 1 and 2 can swing relative to one another, the flywheel elements 1 and 2 approaching one another or remove from each other. In reality, the flywheel elements 1 and 2 perform rotary vibrations relative to one another, in the illustration in FIG. 1 these vibrations are reproduced as purely translatory movements.

The spring arrangement 3 has the spring groups 4 and 5 , the springs of the spring group 4 between abutments 6 on the flywheel element 1 and abutments 7 on an intermediate carrier 8 and the springs of the spring group 5 between further abutments 7 on the intermediate carrier 8 and abutments 9 of the flywheel element 2 are such that the springs are compressed to a greater or lesser extent during relative movements between the intermediate carrier 8 and the flywheel elements 1 and 2, respectively, between an intermediate support abutment 7 and one of the abutments 6 and 9 on the flywheel elements 1 and 2, respectively regardless of the relative direction of movement of the flywheel elements 1 and 2 and the intermediate carrier 8th

The mobility of the intermediate support 8 and the flywheel element 2 relative to one another is limited by stops 10 and counter-stops 11, which are effective in both possible directions of movement, when the intermediate support 8 and flywheel element 2 are x deflected from the center position shown relative to each other by a distance.

The relative mobility between the intermediate carrier 8 and the flywheel element 1 is also limited by stops 12 and counter-stops 13 . The counter-stops 13 are spring-loaded by means of springs 14 on the flywheel element 1 , such that between the flywheel element 1 and the intermediate carrier 8, in addition to the springs 4 , the springs 14 also become effective as soon as the intermediate carrier 8 relative to the flywheel element 1 from the illustrated central position moved by more than one path s .

Finally, a slipping clutch 15 is arranged parallel to the springs of the spring group 4 , which is subject to play, such that the intermediate carrier 8 has a mobility 2 w in all possible positions relative to the flywheel element 1 without the slipping clutch 15 taking effect. In the position shown in Fig. 1, the intermediate carrier 8 can move relative to the flywheel element 1 in each case by a distance w in both directions before the slip clutch 15 takes effect. As soon as the slip clutch 15 becomes effective in a direction of movement of the intermediate carrier 8 relative to the flywheel element 1 , the intermediate carrier 8 can move in the opposite direction relative to the flywheel element 1 by a distance 2 w without actuation of the slip clutch 15 .

The flywheel shown in Fig. 1 is preferably tuned such that the operation shown in Fig. 2 results in behavior. The flywheel elements 1 and 2 may initially be deflected towards one another in one direction. The spring groups 4 and 5 are increasingly compressed, so that they oppose a growing resistance according to the curve section a of the movement of the flywheel elements 1 and 2 until the game w of the slip clutch 15 is consumed. With further movement of the flywheel elements 1 and 2 , only the spring group 5 is initially increasingly compressed, corresponding to the curve section b , since the slip clutch 15 initially prevents further compression of a spring group 4 . The steepness of the curve section b is determined by the spring characteristic of the spring group 5 . With still further movement of the flywheel elements 1 and 2 , the slip clutch 15 can slip, so that again, according to the curve section c, both spring groups 4 and 5 are increasingly compressed until the stops 10 and counter-stops 11 (see FIG. 1) act together and one prevent further compression of the spring group 5 . Accordingly, with further movement of the flywheel elements 1 and 2, only the spring group 4 corresponding to the curve section d is increasingly compressed. As soon as the stops 12 and counter-stops 13 (see FIG. 1) cooperate with each other, the stop springs 14 also become effective, so that a further movement of the flywheel elements 1 and 2 in accordance with the curve section e is opposed to a strongly increasing resistance.

If the flywheel elements 1 and 2 had moved from the position shown in FIG. 1 in the opposite direction, the resistance to the respective movement would be given again by the curve sections a 'to e '.

If the direction of movement of the flywheel elements at the end points E or E 'of the curve sections e or e ' reverses, a hysteresis effect occurs because the slip clutch 15 is initially not effective in this direction of movement. First relax according to the curve sections f and f ', the spring groups 4 and the stop springs 14 until the stops 12 and counter stops 13 lift off from each other with further return movement of the flywheel elements 1 and 2 and the stop springs 14 initially have no influence on the further return movement of the flywheel elements Have 1 and 2 . Then relax first according to the curve sections g and g ', the springs of the spring group 4 further until, according to the curves sections h and h ' in addition to the springs of the spring group 4 and the springs of the spring group 5 are somewhat relaxed, then again the game the slip clutch 15 is consumed, so that with further return movement of the flywheel elements 1 and 2 , only the springs of the spring group 5 can relax again, according to the curve sections i and i 'until the slip clutch 15 slips again and the springs of the spring groups 4 and 5 according to the curve sections j and j ' , can extend to their maximum possible design length. If the movement of the flywheel elements 1 and 2 is continued without changing the direction, the springs of the spring groups 4 and 5 become corresponding to the curve sections k and k ', which continue the curve sections j and j ' in a straight line and straight into the curve sections c and c ' pass, increasingly excited. Then again the curve sections d or d 'and e or e ' etc. are run through.

The flywheel shown in Fig. 1 is so designed that the spring stroke of the spring group 5 stops 10 and counter-stops 11 take effect before the springs of the spring group 4 are compressed so far that the stop springs 14 further movement of the flywheel elements Counteract 1 and 2 .

In the example of FIGS. 3 to 6, the flywheel element 1 is connected to an internal combustion engine, while the flywheel element 2 can be coupled to a drive train via a clutch, not shown.

The flywheel element 2 is mounted on a central hub part 21 of the flywheel element 1 by means of a deep groove ball bearing 20 . The flywheel element 1 consists essentially of two parts, one with the hub part 21 integrally connected part 1 'and an annular disc-shaped part 1 '', which is flanged to part 1 ' by means of a screw collar on the outer circumference.

Between the parts 1 'and 1 ''of the flywheel element 1 remains an annular space open towards the hub part 21 .

In its radially outer region, this annular space has two sections which are approximately circular in cross section and have a relatively large length in the circumferential direction of the flywheel. This on its radial outside by means of a sliding layer 22 lined sections serve as spring chambers for long-stroke coil springs 23 , which form the spring group 4 of FIG. 1. The coil springs 23 have a curved screw axis, the center of curvature of which falls in the axis of the flywheel. In the front ends of the coil springs 23 hat-shaped stop pieces 24 are inserted in the manner shown in FIG. 3.

The coil springs 23 seek these stop pieces 24 against abutment pieces 25 arranged between them on the flywheel element 1 , each of which is formed in pairs opposite to one another with axial spacing on the parts 1 'and 1 ''of the flywheel element 1 as an arc view of the flywheel in axial view. The axial distance between the abutment pieces 25 is less than the outer diameter of the coil springs 23 and the stop pieces 24th

The abutment pieces 25 have opposing windows into which short-stroke helical springs 26 , which correspond to the springs 14 in FIG. 1, are inserted in a cage-like manner. The coil springs 26, whose diameter is greater than the axial distance between the abutment pieces 25, as well as the receiving window arranged them in the abutment pieces 25 tangentially to the flywheel axis. Referring to FIG. 3, the coil springs 26 may be asymmetrically located within the abutment pieces 25, such that the one ends of the abutment pieces 25 in the circumferential direction of the flywheel from the respective ends of the springs 26 have a greater spacing than the other ends.

Between the parts 1 'and 1 ''of the flywheel element 1 , the disc-shaped intermediate carrier 8 is arranged, which has on its outer circumference radial projections 27 which are movable in the space between the abutment pieces 25 . These projections 27 each engage in the space between the springs 23 and 26 , wherein each of the helical springs 23 facing radial edges of the projections 27 on both sides of a helical spring 26 in the circumferential direction have the same distances from one another as the ends of the abutment pieces 25 . Each of the helical springs 26 facing radial edges of adjacent projections 27 have a distance which is greater in the circumferential direction of the flywheel than the length of the helical springs 26 , with a total of 2 s play .

Due to the arrangement shown, the coil springs 23 are compressed at relative rotation between the intermediate carrier 8 and the flywheel element 1 in each case between one of the projections 27 at one end of the coil springs 23 and the abutment pieces 25 at the other end of the coil springs 23 . With sufficient relative rotation, the projections 27 adjacent to the other ends of the coil springs 23 then co-operate with the coil springs 26 , which in this case lie between the latter projections 27 and the radial edges of the coil springs 26 in the abutment pieces 25 opposite them in the axial direction of the coil springs 26 receiving window compressed.

In the illustrated in Fig. 3 arrangement, the intermediate support 8 gersinn relative to the flywheel element 1 in the Time to rotate about a larger angle than in the opposite direction before the cooperating projections 27 a with the screw springs 26. The relative rotation of the intermediate carrier 8 in the clockwise direction occurs in overrun mode, that is to say, for example, when the speed of the engine is increased against the resistance of the drive train.

The radially inner region of the disk-shaped intermediate carrier 8 is arranged axially between two annular disks 28 , which are non-rotatably connected to the flywheel element 2 by means of bolts 29 . Between the annular disks 28 , the bolts 29 carry a thickening or sleeves in order to keep the annular disks 28 axially spaced apart from one another according to FIG. 4.

The bolts 29 or their thickened area or the like. enforce windows 30 arranged in the intermediate carrier 8 , which cooperate with the bolts 29 to limit the rotatability of the intermediate carrier relative to the flywheel element 2 . Overall, the bolts 29 within the window 30 in the circumferential direction of the flywheel 2 x play is available.

Windows 31 are arranged in the annular disks 28 on both sides of the windows 30 tangentially to the flywheel axis. The length of the windows 31 in the circumferential direction has the same dimension as the windows 30 of the intermediate carrier 8 . In the window 31 and 30 short-stroke helical springs 32 are used, which form the spring group 5 in Fig. 1. The diameter of the coil springs 32 is greater than the axial distance between the washers 28 , so that the coil springs 32 are held in a cage-like manner in the windows 31 of the washers 28 . With relative rotation between the intermediate carrier 8 and the flywheel element 2 , the coil springs 32 are compressed between opposite radial edges of the windows 30 and 31 to a reduced length, which corresponds to the length of the overlap area of the windows 30 and 31 in the circumferential direction of the flywheel.

On its inner circumference comprising the hub part 21 of the flywheel element 1 , the intermediate carrier 8 according to FIGS . 5 and 6 has recesses 33 which receive axial extensions 34 'of a friction ring 34 . The axial extensions of the friction ring within the recesses 33 a total of a game 2 w in the circumferential direction of the flywheel. The extensions facing the bearing 20 bear against a support ring 35 with an angular profile, one of whose legs encompassing the hub part 21 abuts the bearing shell of the deep groove ball bearing 20 on the hub part side. The friction ring 34 cooperates with its end facing away from the extensions side with a counter friction ring 36 , which is axially displaceably arranged on the hub part 21 and held non-rotatably by means of angled extensions 36 'relative to the flywheel element 1 by the extensions 36 ' in axial recesses 37 of the Part 1 'of the flywheel element 1 engage. Axially between the part 1 'of the flywheel element 1 and the counter friction ring 36 , an annular plate spring 38 is clamped, which sets the counter friction ring 36 against the friction ring 34 and the latter with its extensions against the support ring 35 , which in turn urges the bearing shell of the bearing 20 urges the hub part 21 against a cover arranged at hub portion 21 annular flange. 39 The plate spring 38 thus has a double function, ie on the one hand it presses the friction ring 34 and the counter friction ring 36 against one another, furthermore the plate spring 38 secures the position of the inner bearing shell of the deep groove ball bearing 20 on the hub part 21 . To increase the friction between the friction ring 34 and the counter-friction ring 36 , friction plates (not shown) can be arranged between these rings.

As soon as the intermediate carrier 8 is rotated relative to the flywheel element 1 to such an extent that the movement play of the extensions of the friction ring 34 in the recesses 33 is consumed, the intermediate carrier 8 takes the friction ring 34 with its further movement, ie the further movement of the intermediate carrier 8 relative to the flywheel element 1 counteracts the frictional resistance of the slip clutch formed by the rings 34 and 36 , which corresponds to the slip clutch 15 in FIG. 1.

Between the inner circumferential edge of part 1 '' of the flywheel element and this inner circumferential edge somewhat under engaging ring step on the flywheel element 2 , a seal 40 may be arranged so that between the flywheel elements 1 and 2 a between the parts 1 'and 1 ''of the flywheel element 1 in- reaching closed annular space is formed, which can hold a lubricant, which is pushed radially outward when the flywheel rotates and thereby fills the annular space outside of an annular surface 41 and thus, above all, fills the space occupied by the helical springs 23 . As a result, in addition to lubrication of these springs 23 , hydraulic damping of the spring movements is also achieved, because when the coil springs 23 are compressed, hydraulic medium must be displaced between the hat-shaped stop pieces 24 .

At low speed, the flywheel shown in Figs. 3 to 6 behaves essentially according to the diagram in Fig. 2. At higher speeds, it should also be noted that the coil springs 23 are pushed due to the centrifugal force with increasing force against the sliding layer 22 and accordingly can only perform suspension strokes against a frictional resistance dependent on the centrifugal force. At higher speed, therefore, the coil springs 23 form a largely rigid connection between the flywheel element 1 and the intermediate carrier 8 , so that the flywheel elements 1 and 2 essentially only against the opposing stand of the coil springs 32 are rotated against each other. This takes into account the fact that at higher speeds only a few vibrations can be excited by the engine anyway, so that the springs 32 are sufficient for vibration decoupling between the engine and the drive train or between the flywheel elements 1 and 2 . Only at lower speeds, the coil springs 23 become increasingly effective, so that the flywheel elements 1 and 2 can perform relatively extensive movements against one another, as is desired at lower speeds, since stronger vibrations can then be excited by the engine. According to the invention, a relatively large path is then available for the vibration decoupling of the flywheel elements 1 and 2 .

Destructive natural oscillations of the intermediate support 8 and excessive movement of the flywheel elements 1 and 2 relative to each other, especially when passing through the resonance range (referred to in Fig. 1 with 15) mainly through the structure formed by the friction rings 34 and 36 slip clutch as well as the coil springs 26 prevents which counteract excessive movement of the intermediate carrier relative to the flywheel element 1 .

Claims (13)

1. Split flywheel with two coaxial flywheel elements, on which the masses of the flywheel are essentially divided, as well as with a flywheel elements coupling, partially playful slip clutch and spring arrangement with an intermediate carrier coaxial with the flywheel elements, which with a flywheel element via a slip clutch and with the two flywheel elements are drive-coupled via separate coil spring groups with different spring rates, one of the coil spring groups consisting of springs with an arc-shaped screw axis whose center of curvature falls into the flywheel axis, characterized in that

• - That the rigid spring group ( 5 ), which couples the intermediate carrier ( 8 ) with the one flywheel element ( 2 ), consists of short-stroke springs ( 32 ),
• - That the soft spring group ( 4 ), which couples the intermediate carrier ( 8 ) with the other flywheel element ( 1 ), is formed by the coil springs ( 23 ) with the arcuate screw axis,
• - That the springs ( 23 ) of the soft spring group ( 4 ) are so soft and long-stroke that they work with centrifugal force-dependent friction by being pushed radially outwards against bearing surfaces on the intermediate carrier ( 8 ) or on the other flywheel element ( 1 ) by the centrifugal force be, and
• - That parallel to the soft spring group ( 4 ) is only a larger relative rotation between the other flywheel element ( 1 ) and the intermediate carrier ( 8 ) effective stop spring ( 14; 26 ) and / or a playful slip clutch ( 15; 34, 36 ) is arranged.

2. Split flywheel according to claim 1, characterized in that the spring groups ( 4 , 5 ) are arranged radially one above the other relative to the flywheel axis. 3. Split flywheel according to one of claims 1 or 2, characterized in that the bearing surfaces for the long-stroke springs ( 23 ) on a flywheel element ( 1 ) are designed as a cross-sectionally U-shaped or circular bed. 4. Split flywheel according to claim 3, characterized in that the bed is lined with a sliding layer ( 22 ) at least on the springs ( 23 ) to the radially outward supporting side. 5. Split flywheel according to one of claims 1 to 4, characterized in that at the end faces of the bearing surfaces are arranged opposite abutment elements ( 25 ) in the axial direction of the flywheel, the distance between them is less than the diameter of the long-stroke coil springs ( 23 ) and which have cutouts or windows tangential to the flywheel axis, in which other helical springs ( 26 ) serving as resilient stops are cage-like, and that the intermediate carrier ( 8 ) with extensions ( 27 ) movable between the abutment elements ( 25 ) with play in The circumferential direction in the space between the long-stroke springs ( 23 ) and the other coil springs ( 26 ) engages. 6. Split flywheel according to one of claims 1 to 5, characterized in that the distance in the circumferential direction of the springs on both sides of the long-stroke screws ( 23 ) arranged extensions ( 27 ) corresponds to the distance of the abutment elements ( 25 ) at the ends of the bearing surfaces . 7. Split flywheel according to one of claims 1 to 6, characterized in that the intermediate carrier ( 8 ) is arranged axially between two on the other flywheel element ( 2 ) arranged disc parts ( 28 ) which have several cutouts or windows tangential to the flywheel axis ( 31 ) have in which the coil springs ( 32 ) of the other spring group ( 5 ) are received in a cage-like manner, and that radial spokes or extensions (between windows 30 ) are arranged on the intermediate carrier ( 8 ) between the coil springs ( 32 ) of this group of springs ( 5 ) . 8. Split flywheel according to one of claims 1 to 7, characterized in that the intermediate carrier ( 8 ) relative to the other flywheel part ( 2 ) can be rotated to a limited extent by bolts ( 29 ) serving to hold the disk parts ( 28 ) with the spokes or Cooperate extensions as stops. 9. Split flywheel according to one of claims 1 to 8, characterized in that the intermediate carrier ( 8 ) with a friction ring part ( 34 ) or annularly arranged friction parts is connected by the friction ring part ( 34 ) or the friction parts with in the axial direction of the flywheel extend extensions in recesses ( 33 ) of the intermediate carrier ( 8 ), and that the friction ring part ( 34 ) or the friction parts are axially clamped against a counter friction part ( 36 ) which is held on a flywheel element ( 1 ). 10. Split flywheel according to one of claims 1 to 9, characterized in that the extensions in the savings ( 33 ) with play in the circumferential direction and / or the counter friction part with play in the circumferential direction are arranged or held net. 11. Split flywheel according to one of claims 1 to 10, characterized in that a central axial extension or hub part ( 21 ) is arranged on a flywheel element ( 1 ) on which, with the interposition of a bearing ( 20 ), the other flywheel element ( 2 ) rotatably gert, and that the inner bearing shell of the bearing ( 20 ) axially against an axial extension or hub part ( 21 ) arranged ring web, ring flange ( 39 ) or the like. is tensioned by the friction ring part ( 34 ) or the friction parts axially between two on the axial extension or hub part ( 21 ) axially displaceable pressure rings or friction rings ( 35 , 36 ) are arranged, one of which is supported on the bearing shell and the other is tensioned in the direction of the bearing shell by means of a spring arrangement, for example by means of a disk spring ring ( 38 ). 12. Split flywheel according to one of claims 1 to 10, characterized in that on a flywheel element ( 1 ) a central axial extension or hub part ( 21 ) is arranged on which the other flywheel element ( 2 ) rotatably with the interposition of a bearing ( 20 ) gert, and that the inner bearing shell of the bearing ( 20 ) against an axial extension or hub part ( 21 ) angeord Neten ring web, ring flange ( 39 ) or the like. is tensioned by the friction ring part ( 34 ) or the friction parts are arranged axially between two pressure or friction rings ( 35 , 36 ), and that the inner bearing shell and the one adjacent to the bearing shell a pressure or friction ring as an abutment of a spring washer or . Like. is arranged, which urges the last-mentioned pressure or friction ring away from the bearing shell against an abutment interacting with the other friction or pressure ring. 13. Split flywheel according to one of claims 1 to 12, characterized in that the long-stroke screw spring ( 23 ) receiving bed is arranged as part of an annular chamber filled with lubricant.